Drive mechanism for shaker conveyers



Dec. 31, 1935.

W. W. SLOANE DRIVE MECHANISM FOR SHAKER CONVEYERS Original Filed Nov.28, 1932 3 Sheets-Sheet l 7' 206127 01 [Vii/jam ZflJ/oa/le M 2. P

Dec. 31, 1935. w w SLOANE 2,026,103

DRIVE MECHANISM FOR SHAKER CONVEYERS Original Filed Nov. 28, 1952 5Sheets-Sheet 2 ECHZQW Zdz'ZZL'a/W ZMJZoona (LQMM a. P

Dec. 31', 1935. w w SLQANE 2,026,103

DRIVE MECHANISM FOR SHAKER CONVEYERS Original Filed Nov. 28, 1932 3Sheets-Sheet 3 Patented Dec. 31, 1935' usirso sTATss PATENT OFFICE DRIVEMECHANKSM FOR SHAKER C'ONVEYERS William W. Sloane, Chicago, Ill.,assignor to Goodman Manufacturing Company, Chicago,

Ill., a corporation of Illinois its 21 Claims. (Cl. 198-220) Thisinvention relates to improvements in drive mechanisms for shakerconveyors of the type utilized for conveying loose material, such ascoal.

Among the objects of the invention are to provide an improvedconstruction and arrangement of the shaker drive whereby minimum headspace or vertical clearance is required, and wherein a portion of theintermediate drive mechanism extends beneath the shaker trough, andreciprocating motion may be transmitted to the shaker trough in avertical plane including the longitudinal axis of said trough.

A further and important object of my invention is to provide an improvedmechanical movement for drive mechanisms of the character described,whereby a plurality of power transmitting devices are interposed betweenthe drive motor and the trough, and arranged to transpose the rotarymotion produced by the motor into a rectilinear motion havingpredetermined changes in acceleration during various parts of its strokeso as to produce a most efficient jigging action for moving loosematerial in one direction along the conveyer trough. As will hereinaftermore fully appear my improved form of mechanical motion is basedprimarily upon certain novel principles of arrangement and relationshipof bell crank members and connecting links, which principles are capableof application in a wide variety of forms not necessarily limited to thespecific form of shaker trough illustrated herein.

In the design of shaker conveyer driving mecha nism, it is oftenpossible to increase the movement of the material alon the pan line byincreasing the maximum forces that are applied to the pan line and tothe various parts of the driving mecha- It is, of course, desirable thatthe material be moved as rapidly as possible and at the same time thestresses be kept to a minimum. Accordingly. another of the principalobjects of my invention is to provide a drive mechanism of the characterdescribed which will move material faster than other drive mechanisms inproportion to the stresses created.

The invention may best be understood by reference to the accompanyingdrawings in which:

Figure 1 is top plan View of one embodiment of my invention with partsof the shaker trough and gear case cover removed, and parts broken awayto show certain features of construction of the main operating parts;

Figure 2 is a transverse section taken along line 22 of Figure 1;

Figure 3 is a longitudinal section taken along line 3-3 of Figure 1;

, movement; and

Figure 6 is a diagrammatic view of the power linkage embodying theprinciple of my improved form of mechanical movement, with the partsarranged as in the shaking mechanism shown in Figure 1.

Referring now to the details of the embodiment of my inventionillustrated in the drawings, and relating particularly to the details ofconstruction wherein an especially compact and simple shaker drive isprovided and overhead clearance is reduced to a minimum, my improvedform of drive consists of a casing I!) which is adapted to rest on themine floor and be suitably securedthereto when in operation by holdingjacks (not shown) or the like in the usual manner. The casing itconsists of a main housing I2 adapted to be positioned at one side of aconveyor trough II and having a reduced laterally extending portion l3adapted to extend beneath said trough and beyond the center linethereof, as clearly shown in Figures 1 and 2.

A motor I5 is mounted on one of the walls of the drive casing. The motorl5 may be of any type, but in the form shown an electric motor isemployed having an armature shaft l6 and drive pinion l1 thereon meshedwith a gear l8 herein rotatable upon a vertically disposed shaft l9supported at its upper and lower ends in antifriction bearing supportsand 2|, respectively. A pinion 22 is keyed on the shaft l9 and drives aspur gear 23 on an upright crank shaft 24 having anti-friction bearingsupports 25, 25 at the upper and lower ends thereof, as shown.

The crank shaft 24 has a crank arm 2! to which is connected ahorizontally disposed connecting rod 28 having its opposite end pivotedon a lever arm 29 forming part of a bell crank member 30.

The bell crank member 30 is pivoted on an upright pin 3! suitablysupported adjacent a base plate 32 of the casing H]. A second arm 33 ofthe bell crank member 30 is slightly longer than the first mentioned arm29, and extends from the pivotal axis of said bell crank member in adirection at a substantial angle from said first mentioned arm butextending generally toward the side where the trough is mounted.

A second connecting link 34 is pivoted on the end of the lever arm 33and extends horizontally into the reduced extension of the casing Illbeneath the trough H where it is connected to an arm 35 of a second bellcrank member 36. This second bell crank member 36 is pivoted on a pin Itwill be especially noted, as one of the features of my improved form ofmechanical movement, that the axis of the first bell crank member 35 isdisposed at one side of the extended axis of the second connecting link34, while the axis of rotation of the second bell crank member 36 isdisposed on the opposite side of the extended axis of said secondconnecting link. The purpose of this particular construction willhereinafter more fully appear in the detail discussion of the mechanicalmovement and its various modifications.

A second arm 39 of the second bell crank member 36 extends at asubstantial angle to its companion arm and toward the center line of thetrough. The second arm 39 of the second bell crank member 36 isconnected at its free end to a double hinged link it, which in turn ispivotally connected to a plunger 4| extending through an elongated guidebearing 43 disposed in a horizontal axis but in a vertical plane whichalso includes the longitudinal axis of the trough H. The trough H isfinally connected to the outer end of the plunger M by means of a doublehinged link M having connection with a suitable bracket 45 mounted onthe undersurface of said trough,

'as shown in Figures 1 and 4.

As a preferred feature of construction to provide ready accessibilitytothe operating parts within the casing If], it will be observed that Isplit said casing upon a horizontal line intersecting the axis of thedriving motor where its armature shaft l6 extends into said casing, asclearly shown in Figure 3. A bottom part 41 of the casing it has aplurality of inwardly extending fiange supports 58, 48 at opposite sidesthereof, upon which are mounted an upwardly arched bracket 59 whichcarries the upper bearing supports 2! and 25 of the shaft l9 and thecrank shaft 25, respectively. The upwardly arched bracket 4-9 issuitably secured to the supporting flanges 48 as by bolts 55, 50.

I also provide a detachable bridge member 5| secured to the supportingflanges 48 between the vertical walls of the upwardly arched bracket 49and secured by bolts 53, 53, as shown in Figure 2. The bridge member 5icarries the lower bearing support 25 of the upright shaft l9, and alsohas a downwardly extending portion 54 which forms the upper bearingsupport for the upright pin 3| which carries the bell crank member 39.An upper part or cover 55 of the casing H3 is detachably connected tothe bottom part M by cap screws,

With the construction described, it will be observed that after thecover 55 is removed, the upwardly arched bracket t9 may be bodilyremoved with its bearing supports 2| and 25, and the bridge member 5|may then be removed in a similar manner so as to permit removal of allof the operating parts contained within the main part of the casing 10.

Referring now more particularly to the novel form and advantages of thespecific arrangement of power transmission mechanism, the linkageemployed in the embodiment illustrated in Figures l, 2, 3, and 4 isshown in diagrammatic form in Figures 5 and 6. It should be understoodthat in order to efficiently move coal or material along the conveyertrough l l, the driving mechanism must impart to said conveyor trough aforward stroke gradually accelerated for a greaterpart of its length,and rapidly decelerated for the remainder of its length; and a backstroke correspondingly but reversely rapidly accelerated for arelatively short portion of its length and gradually decelerated for theremainder of its length. It should further be understood that it isdesirable that the acceleration in the forward stroke, and the combineddeceleration in the forward stroke and acceleration in the returnstroke, be as uniform as possible in order to get the greatest coalmovement in proportion to the maximum accelerating force, it beingunderstood that where the rates of acceleration and deceleration areuniform, the forces of acceleration and deceleration will be uniform.

' When the conveyer pan line is on a relatively level plane, in orderthat material may be moved along said conveyer pan line, it is necessarythat the force of acceleration per unit of weight on the forward strokebe less than the force of deceleration per unit of weight at the otherend of the forward stroke and the force of acceleration on the start ofthe return stroke. It is further desirable that the coefficient offriction of the material to be moved lie somewhere between the values ofthese unit forces or a little less than the lesser force.

Furthermore, in order that a driving mechanism may be capable ofhandling material, the coefficient of friction of which may vary fromtime to time, and in order that movement of the material be not toogreatly affected by moderate changes in speed of the drive motor or bydifferent grades in different portions of the pan line, it is desirablethat the difference between the forces of acceleration on the forwardstroke and the forces of deceleration at the other end of the forwardstroke and the forces of acceleration at the start of the return strokebe sufiicient that the lower unit force; that is, the force ofacceleration of the forward stroke be below the coefficient of frictionof the material, and the maximum force; that is, the force ofdeceleration at the other end of the forward stroke and the force ofacceleration at the start of the return stroke be above the ccefrlcientof friction of the material in whatever combinations of varyingcoefficient of friction of the material, variations in speed of thedrive motor and variation in grade in the pan line may occur.

With reference now in particular to Figure 5, Diagrams A, B, C, D, and Eillustrate several forms and combinations of mechanisms forreciprocating a conveyor trough and moving material therealong. DiagramA shows a simple crank 7' and connecting rod is connected to across-head Z. This mechanism will impart a reciprocatory conveyingaction to a conveyer trough for moving material therealong. The shorterthe connecting red It, the greater will be the difference between theaverage forces at the two ends of the stroke; and the longer theconnecting rod k, the smaller the difference between these forces willbe. One of the chief disadvantages to such a motion, however, is that ifthis mechanism is proportioned to give a wide difference between theforces at the two ends of the stroke, each of these forces becomenon-uniform to an undesirable degree, especially the lesser forces.

Another mechanism commonly used for imparting a conveying action to aconveyer trough for moving material therealong is illustratedby DiagramB of Figure 5. In this diagram, a connecting rod m is driven by asuitable crank (not shown) in the same manner the connecting rod is inDiagram A, is driven by the crank 7'. In order that the moving effect ofthe mechanism may be studied independently of any moving action it mayreceive from the connecting rod driving the mechanism, the connectingrod m has been considered to be of infinite length. The connecting rod mis connected to one lever arm n of a bell crank member and moves thislever arm of said bell crank member through equal angles from a lineextending through the center of oscillation of said bell crank memberand substantially perpendicular to said connecting rod. A connectinglink 10 is connected to another lever arm q of the bell crank member 0,which lever arm moves to one side of a line extending through the axisof pivotal movement of said bell crank member and substantially at rightangles to the average position of said connecting link.

It being considered that the lengths of the connecting rod m andconnecting link p are such that their angular motion is negligible, thestudy of the mechanism shown in Diagram B has demonstrated that thegreater the angle through which the lever arm q is moved to one side ofa line drawn through the center of oscillation of the bell crank member0 and perpendicular to the average position of the connecting link pwithin workable limits, the greater will be the dilierence between theforces of acceleration and deceleration at the two ends of the stroke.The disadvantages of the mechanism shown in Diagram B, however, are thesame as those in the mechanism shown in Diagram A; namely, that theforces become non-uniform when the mechanism is proportioned to give awide difference between the forces at the two ends of the stroke.

When the mechanism shown in Diagram B is combined with the mechanismshown in diagram A and the connecting rod connecting these twomechanisms together is relatively short, the characteristics of theresulting action are similar to those in Diagrams A and B and theproportion of the non-uniformity of the forces is not much altered forthe same difference between the forces.

Considering now the mechanism shown in Diagram C, a connecting rod s isconnected to one lever arm t of a bell crank member 11,. Considering theconnecting rod 3 as being driven by a suitable crank and as being ofinfinite length so its angular movement is negligible, said connectingrod moves the lever arm t of the bell crank member u to one side of aradial line extending from the axis of pivotal movement of said bellcrank member and substantially perpendicular to said connecting rod. Aconnecting link 22 is connected to another lever arm to of the bellcrank member u and said lever arm and connecting link are moved throughequal angles from a radial line extending through the axis of pivotalmovement of the bell crank member u and sub stantially at right anglesto said connecting link in its average position.

The shaking motion produced by the mechanism shown by Diagram C ofFigure 5 is similar to that produced by the mechanism shown by Diagram3, with the exception that it is possible to obtain a greater diiferencebetween the forces at both ends of the stroke with the same degree ofnon-uniformity or to obtain the same difierence between the forces atboth ends of the stroke with a greater degree of uniformity. This isparticularly true during the accelerating portion of the forward stroke.

It has been found that when the mechanism shown by Diagram C of Figure 5isdriven from a crank shaft by a connecting rod of a length comparableto the length of the connecting rod is in Diagram A, that the effect ofthe connecting rod angle on the resulting motion is such as to destroythe advantages of this mechanism over those shown in Diagrams A and B.

It is therefore apparent that of the three usual methods of drivingshaking conveyors, that the most desirable is that shown by Diagram Cwhen this mechanism is driven by a connecting rod having little or noangular motion.

Angularity of the connecting rod s is reduced by the addition of themechanism shown by Diagram B to the mechanism shown by Diagram C andpositioning said mechanisms with respect to each other and driving theconnecting rod s from the bell crank member 0 in a manner which willhereinafter be more fully described.

Referring now in particular to Diagram D of Figure 5 in which themechanisms shown by Diagrams A, B, and C have been combined, theconnecting rod 7c and crank 7', as well as the bell crank members 0 andu, each contribute to the difference between the forces at the two endsof the stroke. In order to obtain the greatest difference between theforces at the two ends of the stroke, it is necessary that the parts beso assembled with relation to each other that the higher forces ofacceleration and deceleration of each unit occur at the same end of thestroke, and that the lower forces of acceleration and deceleration ofeach unit occur at the oth r end of the stroke. It is apparent that thegreater forces of acceleration and deceleration of the bell crankmembers 0 and u must occur at the same time or else the effects of onewill destroy the effect of the other, and in order that these forces mayoccur at the same time, and in order that angular motion of theconnecting rod 8 may at the same time be reduced to a minimum, thepivotal axes of said bell crank members must be placed on opposite sidesof the longitudinal axis of said connecting rod.

While it is possible to place both of the pivotal axes of the bell crankmembers '0 and u on the same side of the longitudinal axis of theconnecting rod 5, and in so doing reduce the angular motion of saidconnecting rod to zero, it has been found that with this arrangement thehigher forces of each of said bell crank members will occur at oppositeends of the stroke and the effect of one will destroy the effect of theother.

It has been found that a combination of two or moreelements, eachproducing a slight difference in accelerating forces, will give a finalmotion wherein the difference between the accelerating forcesapproximate the sum or" those obtained from each of the elements and thematerial moving ability of the final motion will be superior inproportion to the maximum moving forces which might be obtained from anysingle unit so proportioned as to give the same difference between thetwo average forces.

The mechanisms shown by Diagrams A, B, and C have previously beencombined into one conveyer drive unit in such a manner that the forcesof acceleration occur at the same end of the stroke, but angularmovement of the connecting rod connecting the two bell crank memberstogether spoils the final conveying effect and while the final movementmay be an improvement over that produced by any one single mechanism orcombination of any two of these mechanisms, the final conveying eifectis not one which has a maximum coal moving ability for the same maximumforce.

In order to minimize angular movement of the connecting link 8connecting the bell crank members o and u together, and in order toobtain the greater accelerating force for the two bell crank members atthe same end of the stroke, the pivotal axes of said bell crank membershave been arranged on opposite sides of the longitudinal axis of saidconnecting link in such a manner that the major portion of the arethrough which the lever arrnq of the bell crank member 0' moves is in aposition clockwise from a line extending through the center ofoscillation thereof and substantially perpendicular to the averageposition of said connecting link, while the major portion of the arethrough which the lever arm t of the bell crank member 11. moves is in aposition clockwise from a line extending through the center ofoscillation of said second mentioned bell crank member and substantiallyperpendicular to an average position of said connecting link from saidfirst mentioned lever arm of said first mentioned bell crank member.

While the drawings show the entire arc through which the lever arms qand 15 travel in a position clockwise from perpendicular lines passingthrough the centers of oscillation of the bell crank members 0 and u,and perpendicular to the average position of the connecting rod 8, itshould be understood that the entire portion of the arcs need not be sopositioned as long as the major portions of the arcs are in a positionclockwise from said aforementioned perpendicular lines. It should alsobe understood that the drive mechanism may be so arranged that the majorportions of the arcs are in positions counter-clockwise from saidaforementioned perpendicular lines without afiecting the final driveaction of the mechanism.

It may thus be seen that the element shown by Diagram C, when combinedwith the elements shown by Diagrams A and B, and when operated by aconnecting rod having a minimum amount of angular motion, produces .amore desirable final motion than has formerly been produced wherein agreater coal or material moving force is provided in proportion to themaximum accelerating force.

With reference to Diagram E of Figure 5, said diagram is inserted toillustrate the fact that the positions of the bell crank members 0 and uwith respect to each other may be changed without materially changingthe elfect of the drive action as long as the axes of pivotal movementof the bell crank members 0 and u .are on opposite sides of thelongitudinal axis of the connecting link 8 connecting these bell crankmembers together; and as long as the same angular relation at both endsof the stroke between the lever arms q and t of the bell crank members 0and u, respectively, and the longitudinal axis of the connecting rod .9are maintained at both ends of the stroke.

In Diagram E, the bell crank member 1/, has been moved on the oppositeside of the crank from the bell crank member 0 and the lever arms q andt have been connected together by the connecting rod 8, Whoselongitudinal axis is between the axes of oscillation of said bell crankmembers. It may thus be seen that angular movement of the bell crankmembers 0 and u is substantially the same as in Diagram D and that thearrangement shown in Diagram E is of a more compact form than that shownin Diagram D, and while the angular relation between the lever arms qand t of the bell crank members o and u are the same with respect to thelongitudinal axis of the connecting rod 8 at both ends of the stroke inDiagrams D and E, there will be a slight difference in their angularrelations during the stroke. This difierence is reduced as the length ofthe connecting rod s is increased but for any practical connecting rodlength it does not result in any material change in the final motion.

Referring now to Figure 6 showing diagrammatically the arrangement ofdrive mechanism shown in Figures 1 to- 4, inclusive, and the developmentthereof from the arrangement shown by solid lines in Diagram E of Figure5, said drive arrangement is developed by first projecting the firstlever arm n of the first bell crank member 0 together with theconnecting rod 7c and crank i .as a unit about the axis of pivotalmovement of said bell crank member until said lever arm of said bellcrank member and crank and connecting rod are positioned in the desiredrelationship. It should be noted that in the projected form the angle a,between the first lever arm n of the first bell crank member 0 and theextended connecting rod is is the same .as formerly. The second leverarm 11 of the first bell crank member 0, together with the connectingrod s and second bell crank member u, are likewise projected about theaxis of oscillation of the bell crank member 0 until positioned in thedesired relationship. Here, again, the angle b between the second leverarm q of the first bell crank member 0 and the extended longitudinalaxis of the connecting rod sis maintained and the angle 0 between thefirst lever arm t of the second bell crank member u and connecting rod 8is maintained. When in such a position, the second lever arm 20 of thesecond bell crank member u is projected about the axis of pivotalconnection of said bell crank member until the required position isreached. In this case the angle d, between the lever arm to and thedriving member connected thereto, is maintained.

Thus 7' corresponds to the crank 25, k to the connecting rod 28, n tothe first lever arm 29 of the bell crank member 38, q to the secondlever arm 33 of said bell crank member, t to the first lever arm 35 ofthe second bell crank member 36, w to the second lever arm 39 of saidbell crank member, and o to the double hinge link 48.

It may thus be seen that the angles between the lever arms of each bellcrank member may be changed so as to have any desired relationship withrespect to each other as long as the crank 2s and lever arms of the bellcrank members 36 and 36 are so arranged that the same angular relationis maintained between said lever arms and the connecting rods connectedthereto at both ends of the stroke so that the forces of accelerationand deceleration of the parts occur at the same time and angularmovement of the connecting rod M is reduced to a minimum.

It may thus be seen that my invention provides a driving mechanism of asimple construction consisting of a combination of a driving crank andconnecting rods Ild bell crank members placed in such relation xvithrespect to each other as to produce accelerated and retarded forward andbackward strokes of reciprocating motion of a more efiicient characterthan has formerly been provided, which mechanism is so arranged as tocause the acceleration of the forward stroke and deceleration of theforward stroke and acceleration of the rearward stroke to be as uniformas possible for any given ratio between the average forward and backwardforces of acceleration and deceleration and thus provide a conveyingmechanism which will move material along a pan line in the mostefiicient manner possible without imparting unduly heavy strains on theparts of the mechanism and that this mechanism is so constituted as tobe capable of being arranged in various forms without impairing theefiiciency of the device so as to be adapted for use in varyingconditions and more particularly conditions where space is necessarilylimited.

While I have herein shown and described one form of my invention, I donot wish to be limited to the precise details of construction orarrangement of parts herein shown and described, excepting asspecifically limited in the appended claims.

I claim as my invention:

1. In a shaker conveyer operating mechanism, the combination with areciprocably driven conveyer trough, of two devices reciprocably movableabout fixed pivotal axes, mechanism connecting one of said devices tosaid conveyer trough and a connecting member connecting said devicestogether, the axes of pivotal movement of said devices being on oppositesides of the longitudinal axis of said connecting member.

2. In a shaker conveyer operating mechanism, the combination with areciprocably driven conveyer trough, of a rotatable member, two devicesreciprocably movable about fixed pivotal axes, mechanism connectingsaid. rotatable member to one of said devices, mechanism connecting theother of said devices to said conveyer trough, and a connecting memberconnecting said devices together, said member being so located that theaxes of pivotal movement of said devices are on opposite sides of thelongitudinal axis of said conneoting member.

3. In a shaker conveyer operating mechanism, the combination with areciprocably driven member, of a rotatable member, two devicesreciprocably movable about parallel pivotal axes, each of said deviceshaving lever arms extending outwardly from the pivotal axis thereof, aconnec tion between one of said lever arms on one of said devices tosaid rotatable member for oscillating said device, a connection betweenone of said lever arms on said other device and said driven member fordriving said driven member, and means for connecting the other leverarms of said devices together comprising a connecting member arranged sothe axes of pivotal movement of said devices are on opposite sides ofthe longitudinal center line of said connecting member.

4. In a shaker conveyer operating mechanism, the combination with areciprocably driven member, of a rotatable member, of two bell crank members, a connection between said rotatable member and one lever arm ofone of said bell crank members for oscillating said bell crank member, aconnection between one arm of said other bell crank member and saiddriven member, and a connection between the other lever arms of saidbell crank members comprising a connecting member so disposed that itslongitudinal center line is between the axes of pivotal movement of saidbell crank'members.

5. In ashaker conveyer operating mechanism, a reciprocably drivenmember, a rotatable crank member, two bell crank members pivotallymove.-

ble about parallel axes, a connection between said rotatable crankmember and one lever arm of one of said bell crank members, a connectionbetween one. lever arm of said other bell crank member and saidreciprocably driven member, and a connection between the other leverarms of said bell crank members comprising a connecting member sodisposed that its extended longitudinal center line is between the axesof pivotal movement of said bell crank members.

6. A shaker conveyer drive comprising a crank arm, a driven membercomprising a reciprocating conveyer trough, and means connectible withsaid crank arm for imparting accelerated and retarded backward andforward strokes of reciprocating motion to said driven member comprisinga rocking member connected to said crank arm and driven therefrom,another rocking member spaced from said first mentioned rocking memberand mounted for movement about a fixed pivotal axis, a connection fromsaid rocking member to said driven member and a connection between saidrocking members so arranged that a line passing through the points ofconnection of said connection to said rocking members is intermediatethe axes of pivotal movement of said rocking members.

'7. A shaker conveyer drive comprising a crank arm, a driven membercomprising a reciprocating conveyer trough, and means connectible withsaid crank arm for imparting accelerated and retarded backward andforward strokes of reciprocating motion to said driven member comprisinga rocking member, a connecting member connecting said crank arm withsaid rocking member, another rocking member rockable about an axisparallel to the axis of pivotal movement of said first mentioned rockingmember, a connection from said rocking member to said driven member, andan operative connection between said rocking members whereby rockingmovement of said first mentioned rocking member will cause anaccelerated and retarded rocking movement of said second mentionedrocking member having a uniform rate of retardation and acceleration ateach end of the stroke comprising a connecting member connecting saidrocking members together in such a manner that said connecting member isintermediate the axes of pivotal movement of said rocking members.

8. A shaker conveyer drive comprising a crank arm, a driven membercomprising a reciprocating conveyer trough, and means connectible withsaid crank arm for imparting accelerated and retarded backward andforward strokes of reciprocating motion to said driven member comprisinga rocking member, a connecting member connecting said crank arm withsaid rocking member, the point of pivotal connection of said connectingmember to said rocking member being so arranged with respect to the axisof pivotal movement of said rocking member that said point oscillates atequal angles to a radial line extending through the axis of said rockingmember and perpendicular to the longitudinal center line of saidconnecting member when said crank is in a dead center position, anotherrocking member spaced from said first mentioned rocking member, aconnecting member connecting said other rocking member to said drivenmember, the point of pivotal connection of said other rocking member tosaid connecting member being so arranged with respect to the axis ofpivotal movement of said rocking member that it oscillates at equalangles to each side of a radial line extending through 'tudinal axis ofsaid driven member, and a connection between said rocking memberscomprising a connecting member connected to said rocking members at itsends, the points of connection of said connecting member to said rockingmembers being such that said points oscillate to one side of extendedradial lines passing through the center of pivotal movement of saidrocking members and perpendicular to the average position of saidconnecting member.

. 9. A shaker conveyer drive comprising a crank arm, a driven membercomprising a reciprocating conveyer trough, and means connectible withsaid crank arm for imparting accelerated and retarded backward andforward strokes of reciprocating motion to said driven member comprisinga rocking member, a connecting member connecting said crank arm withsaid rocking member, the point of pivotal connection of said connectingmember to said rocking member being so arranged with respect to the axisof pivotal movement of said rocking member that said point oscillates-atequal angles to a radial line extending through the axis of said rockingmember and perpendicular to the longitudinal center line of saidconnecting member when said crank is in a dead center position, anotherrocking member spaced from said first mentioned rocking member, aconnecting member connecting said other rocking member to said drivenmember, the point of pivotal connection of said other rocking member tosaid connecting member being so arranged with respect to the axis ofpivotal movement of said rocking member that it oscillates at equalangles to each side of a radial line extending through the axis ofpivotal movement of said rocking member and perpendicular to an extendedlongitudinal axis of said driven member, and a connection between saidrocking members comprising a connecting member connected to said rockingmembers at its ends, the points of connection of said connecting memberto said rocking members being such. that said points oscillate to oneside of extended radial lines passing through the center of pivotalmovement of said rocking members and perpendicular to the averageposition of said connecting member, and said connecting member being soarranged that the axes of pivotal movement of said rocking members areon opposite sides of its longitudinal center line.

10. In a shaker conveyer drive, a rotatable member, a driven membercomprising a reciprocating conveyer trough, a rocking member, a connecting member for connecting said rocking member with said rotatablemember, the point of connection of said connecting member to saidrocking member being so arranged with respect to the axis of pivotalmovement of said rocking member that said point may oscillate at equalangles to a radial line extending through the axis of said rockingmember and perpendicular to the longitudinal center line of saidconnecting member when the point of connection of said rotatable memberto said connecting member is in a dead center position, another rockingmember spaced from said first mentioned rocking member and havingconnection with said driven member, and a connection between saidrocking members comprising a connecting member connected to said rockingmembers at its ends, the points of connection of said connecting memberto said rocking members being such that said points oscillate to oneside of extended radial lines passing through the center of pivotalmovement of said rocking members and perpendicular to the averageposition of said connecting member.

11. In a shaker conveyer drive, a rotatable member, a driven membercomprising a recipro- 5 cating conveyer trough, a rocking member, aconnecting member for connecting said rocking member with said rotatablemember, the point of connection of said connecting member to saidrocking member being so arranged with respect 10 to the axis of pivotalmovement of said rocking member thatsaid point may oscillate at equalangles to a radial line extending through the axis of said rockingmember and perpendicular to the longitudinal center line of saidconnecting mem- 15 er when the point of connection of said rotatablemember to said connecting member is in a dead center position, anotherrocking member spaced from said first mentioned rocking member andhaving connection with said driven member, and 20 a connection betweensaid rocking members comprising a connecting member connected to saidrocking members at its ends, the points of connection of said connectingmember to said rocking members being such that said points oscillate 25to one side of extended radial lines passing through the center ofpivotal movement of said rocking members and perpendicular to theaverage position of said connecting member, and said connecting memberbeing so arranged that the 30 axes of pivotal movement of said rockingmembers are on opposite sides of the longitudinal center line of saidconnecting member.

12. In a shaker conveyer drive, a rotatable crank, a driven membercomprising a reciprocat- 35 ing conveyer trough, a bell crank member, aconnecting link for connecting one arm of said bell crank member to saidrotatable crank, said arm of said bell crank member being oscillatableat equal angles to a radial line extending through 40 the axis ofpivotal movement of said bell crank member and perpendicular to saidconnecting link when said rotatable crank is in a dead center position,another bell crank member spaced from said first mentioned bell crankmember and oscil- 45 latable about an axis parallel to the axis ofpivotal movement of said first mentioned bell crank member, a connectionfrom one lever arm of said last mentioned bell crank member to saiddriven member and a connection from the other lever 50 arm of said lastmentioned bell crank member to the second lever arm of said firstmentioned bell crank member, said connection being such and said bellcrank members being so arranged that the lever arm of said lastmentioned bell crank 55 member having connection with said driven memberoscillates at equal angles to a radial line extending through the axisof pivotal movement of said last mentioned bell crank member andperpendicular to the longitudinal center line of said 0 driven member.

13. In a shaker conveyer drive, a rotatable crank, a driven membercomprising a reciprocating conveyer trough, a bell crank member, aconnecting link for connecting one arm of said bell 5 crank member tosaid rotatable crank, said arm of said bell crank member beingoscillatable at equal angles to a radial line extending through the axisof pivotal movement of said bell crank member and perpendicular to saidconnecting 70 link when said rotatable crank is in a dead centerposition, another bell crank member spaced from said first mentionedbell crank member and oscillatable about an axis parallel to the axis ofpivotal movement of said first mentioned bell 75 J crank member, aconnection from one lever arm of said last mentioned bell crank memberto said driven member and a connecting link connecting the other leverarm of said last mentioned bell crank member to the second lever arm ofsaid first mentioned bell crank member, said second lever arm of saidfirst mentioned bell crank mem her being so arranged with respect tosaid first lever arm of said bell crank member as to oscillate to oneside of a radial line extending through the pivotal axis of said bellcrank member and perpendicular to the average position of thelongitudinal center line of said last mentioned connecting link and saidconnecting link being so arranged as to be between the centers ofoscillation of said bell crank members.

14. In a shaker conveyer drive, a rotatable crank, a driven membercomprising a reciprocating conveyer trough, a bell crank member, aconnecting link for connecting one arm of said bell crank member to saidrotatable crank, said arm of said bell crank member being oscillatableat equal angles to a radial line extending through the axis of pivotalmovement of said bell crank member and perpendicular to said connectinglink when said rotatable crank is in a dead center position, anotherbell crank member spaced from said first mentioned bell crank member andoscil latable about an axis parallel to the axis of pivotal movement ofsaid first mentioned bell crank member, a connection from one lever armof said last mentioned bell crank member to said driven member and aconnecting link connecting the other lever arm of said last mentionedbell crank member to the second lever arm of said first mentioned bellcrank member, said last mentioned lever arms of said bell crankmemberbeing so arranged with respect to said first mentioned lever arms as tooscillate to one side of radial lines extending from the axes ofoscillation of said bell crank members and perpendicular to the 4average longitudinal center line of said connecting link and said leverarm of said second bell crank member having connection with said drivenmember being so disposed with respect to said other lever arm as tooscillate at equal angles to a radial line perpendicular to thelongitudinal center line of said driven member and extending through theam's of oscillation of said bell crank member.

15. In a shaker conveyer drive, a rotatable crank, a driven membercomprising a reciprocating conveyer trough, a bell crank member, aconnecting link for connecting one arm of said bell crank member to saidrotatable crank, said arm of said bell crank member being oscillatableat equal angles to a radial line extending through the axis of pivotalmovement of said bell crank member and perpendicular to said connectinglink when said rotatable crank is in a dead center position, anotherbell crank member spaced from said first mentioned bell crank member andoscillatable about an axis parallel to the axis of pivotal movement ofsaid first mentioned bell crank member, a connection from one lever armof said last mentioned bell crank member to said driven member, aconnecting link connecting the other lever arm of said last mentionedbell crank member to the second lever arm of said first mentioned bellcrank member, said connecting link being so arranged as to beintermediate the axes of oscillation of said bell crank members so saidfirst mentioned bell crank member may move said connecting link in apath in which its positions are substantially parallel at opposite endsof the stroke.

16. In a shaker conveyer drive, a rotatable crank, a driven membercomprising a reciprocating conveyer trough, a bell crank member, aconnecting link for connecting one arm of said bell crank member to saidrotatable crank, said arm of said bell crank member being oscillatableat equal angles to a radial line extending through the axis of pivotalmovement of said bell crank member and perpendicular to said connectinglink when said rotatable crank is in a dead center position, anotherbell crank member spaced from said first mentioned bell crank member andoscillatable about an axis parallel to the axis of pivotal movement ofsaid first mentioned bell crank member, a connection from one lever armof said last mentioned bell crank member to said driven member, aconnecting link connecting the other lever arm of said last mentionedbell crank meinher to the second lever arm of said first mentioned bellcrank member, said last mentioned lever arms being so arranged withrespect to said first mentioned lever arms as to oscillate to one sideof radial lines extending from the axes of oscillation of said bellcrank members and perpendicular to the average longitudinal center lineof said connecting link, and said connecting link being so arranged asto be intermediate the axes of oscillation of said bell crank members.

3.7. In a shaker conveyer drive, a rotatable.

crank, a driven member comprising a reciprocating conveyer trough, abell crank member, a connecting link for connecting one arm of said bellcrank member to said rotatable crank, said arm of said bell crank memberbeing oscillatable at equal angles to a radial line extending throughthe axis of pivotal movement of said bell crank member and perpendicularto said connecting link when said rotatable crank is in a dead centerposition, another bell crank member spaced from said first mentionedbell crank member and oscillatable about an axis parallel to the axis ofpivotal movement of said first mentioned bell crank member, a connectionfrom one lever arm of said last mentioned bell crank member to saiddriven member, a connecting link connecting the other lever arm of saidlast mentioned bell crank member to the second lever arm of said firstmentioned bell crank member, said last mentioned lever arms being soarranged with respect to said first mentioned lever arms as to oscillateto one side of radial lines extending from the axes of oscillation ofsaid bell crank members and perpendicular to the average longitudinalcenter line of said connecting link, said connecting link being soarranged as to be intermediate the axes of oscillation of said bellcrank members and said lever arm of said second bell crank member havingconnection with said driven member being so disposed with respect tosaid other lever arm as to oscillate at equal angles to a radial lineextending through the axis of oscillation of said bell crank member andperpendicular to the longitudinal center line of said driven member.

18. In a shaker conveyer operating mechanism, a conveyer trough, meansfor reciprocably moving said conveyer trough comprising a driven memberdisposed beneath said conveyer trough and reciprocably movable in aplane coincident with the longitudinal axis of said conveyer trough, ahousing having a reduced portion extending beneath said conveyer trough,a guide in said reduced portion of said housing for guiding said drivenmember in a plane coincident with the longitudinal axis of said conveyertrough, and drive mechanism mounted in said housing for driving saiddriven member including a motor supported by said housing, a rotatablemember driven thereby, and a connecting member reciprocably movable in ahorizontal plane extending into said reduced portion of said housing andhaving connection with a bell crank member mounted in said reducedportion of said housing for pivotal movement about a vertical axisintersecting said conveyer trough and said bell crank member havingconnection with said driven member.

19. In a shaker conveyer operating mechanism, a conveyer trough, meansfor reciprocably moving said conveyer trough comprising a driven memberdisposed beneath said conveyer trough and reciprocably movable in aplane coincident with the longitudinal axis of said conveyer trough, ahousing having a reduced portion extending beneath said conveyer trough,a guide in said reduced portion of said housing for guiding said drivenmember in a plane coincident with c the longitudinal axis of saidconveyer trough, and

drive mechanism mounted in said housing for driving said driven memberincluding a motor supported by said housing, a rotatable member driventhereby, a bell crank member oscillated by said rotatable member about avertical axis, an-

other bell crank member mounted in the reduced portion of said housingfor oscillation about a vertical axis, an operative connection betweensaid bell crank members and a connection between said last mentionedbell crank member and said driven member.

20. In a shaker conveyer operating mechanism, a conveyer trough, anddrive mechanism for reciprocably driving said conveyer trough comprisinga housing, a reduced portion of which extends beneath said conveyertrough, an elongated guide in said reduced portion of said housingdisposed in a horizontal axis but in a Vertical plane which alsoincludes the longitudinal axis of said conveyer trough, a plungerslidable in said guide,

a connection between said plunger and conveyer trough and means forreciprocably moving said plunger including a motor, a bell crank memberdriven thereby, a second bell crank member pivoted in said reducedportion of said housing, a connecting member connecting said bell crankmembers together, and a connection from said last-mentioned bell crankmember to said plunger.

21. In a shaker conveyer operating mechanism, a conveyer trough, anddrive mechanism for reciprocably driving said conveyer trough comprisinga housing, a reduced portion of which extends beneath said conveyertrough, an elongated guide in said reduced portion of said housingdisposed in a horizontal axis but in a vertical plane which alsoincludes the longitudinal axis of said conveyer trough, a plungerslidable in said guide, a connection between said plunger and conveyertrough and means for reciprocably moving said plunger including a motor,a bell crank member driven thereby, a second bell crank member pivotedin said reduced portion of said housing, a connecting member connectingsaid bell crank members together, said connecting member having itslongitudinal axis disposed intermediate the axis of pivotal movement ofsaid bell crank members and extending into said reduced portion of saidhousing, and a connection from said lastmentioned bell crank member tosaid plunger.

WILLIAM W. SLOANE.

